US11199246B2 - Automatic transmission - Google Patents

Automatic transmission Download PDF

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Publication number
US11199246B2
US11199246B2 US17/033,304 US202017033304A US11199246B2 US 11199246 B2 US11199246 B2 US 11199246B2 US 202017033304 A US202017033304 A US 202017033304A US 11199246 B2 US11199246 B2 US 11199246B2
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United States
Prior art keywords
rotating member
extending part
extending
automatic transmission
power transmission
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US17/033,304
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US20210116004A1 (en
Inventor
Akira Hashimoto
Yasuo Miura
Takeyuki Tanaka
Tomoya NAKANO
Kazuhiro Yamada
Hiroyuki Enoki
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Mazda Motor Corp
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Mazda Motor Corp
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Assigned to MAZDA MOTOR CORPORATION reassignment MAZDA MOTOR CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MIURA, YASUO, ENOKI, HIROYUKI, HASHIMOTO, AKIRA, NAKANO, TOMOYA, TANAKA, TAKEYUKI, YAMADA, KAZUHIRO
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

Definitions

  • the present disclosure relates to an automatic transmission.
  • automatic transmissions mounted on vehicles each include a transmission gear mechanism, and a friction engagement device which realizes a plurality of gear stages by switching a power transmission path of the transmission gear mechanism.
  • the friction engagement device includes a clutch which connects and disconnects power between a pair of rotating elements, and a brake which locks rotation of one of the rotating elements.
  • the clutch is a multiple-disk clutch having a plurality of friction plates, and is provided with, as rotating members, a drum member and a hub member.
  • the drum member spline engages with some of the friction plates at an outer circumference thereof so that the friction plates are axially movable, and is coupled to a given rotating element of the transmission.
  • the hub member spline engages the remaining friction plates at an inner circumference thereof so that the friction plates are axially movable, and is coupled to another given rotating element of the transmission.
  • the brake has a similar configuration as the clutch, the brake is different in that one of the drum member and the hub member is fixed to a transmission case.
  • the power transmission part may be considered to form the power transmission part from a ferrous material and form other parts from an aluminum-based material, and join these parts together.
  • it since it is difficult to join parts made of different materials (ferrous and aluminum-based materials) by welding, it may be considered, for example, to join these parts at a caulking part by using mechanical clinching, as disclosed in JP2019-104018A.
  • the caulking part for the mechanical clinching is formed with a protrusion which protrudes by recessing one of the members toward the other member.
  • a joining part which is formed by joining one member and the other member is increased in the dimension at the part where the protrusion is formed.
  • the caulking part is formed by recessing in the axial direction of the automatic transmission, the size of the automatic transmission increases in the axial direction.
  • the present disclosure is made in view of the above situation, and one purpose thereof is to provide an automatic transmission, which is capable of suppressing a dimensional increase in an axial direction, while forming a rotating member which constitutes a part of a clutch or a brake by axially joining members made of different materials at a caulking part via mechanical clinching.
  • the present disclosure is configured as described below.
  • an automatic transmission which includes a first rotating member configured to transmit power between a first pair of members including at least one rotating element, and a second rotating member configured to transmit power between a second pair of members including at least one rotating element.
  • the first rotating member includes an outer rotating member and an inner rotating member located radially inward of the outer rotating member.
  • the outer rotating member has a first outer power transmission part configured to give and receive power to and from one of the first pair of members at a circumferential part formed in a cylindrical shape, and an outer extending part extending radially inward from the first outer power transmission part.
  • the inner rotating member is made of a different material from the outer rotating member, and has a first inner power transmission part configured to give and receive power to and from the other member of the first pair of members, and an inner extending part extending radially outward from the first inner power transmission part.
  • the outer extending part and the inner extending part of the first rotating member are coupled through a first extending part formed by joining the outer extending part and the inner extending part to each other in an axial direction of the automatic transmission at a caulking part via mechanical clinching.
  • the second rotating member includes a second outer power transmission part configured to give and receive power to and from one of the second pair of members at a circumferential part formed in a cylindrical shape, a second inner power transmission part located radially inward of the second outer power transmission part and configured to give and receive power to and from the other member of the second pair of members, and a second extending part extending radially inward from the second outer power transmission part and continuing to the second inner power transmission part.
  • the first extending part and the second extending part are adjacent to each other in the axial direction.
  • the caulking part has a protrusion protruding by being recessed from the first extending part toward the second extending part.
  • the second extending part has a recess indented on an opposite side of the first extending part. At least a part of the protrusion is located inside the recess.
  • the first rotating member can be formed by appropriately joining the outer rotating member and the inner rotating member, which are made of different materials, at the caulking part.
  • the first rotating member can be set so that each part is made of the suitable material, it is possible to reduce weight, while securing strength.
  • the outer rotating member and the inner rotating member can be joined without accompanying, for example, formation of spline-engagement teeth and without using subsidiary materials, the cost can be reduced.
  • the protrusion is formed in the caulking part of the first extending part, which joins the outer extending part and the inner extending part, at least a part of the protrusion is located inside the recess formed in the second extending part.
  • the first extending part can be disposed close to the second extending part, while preventing the protrusion of the caulking part from interfering with the second extending part. Therefore, it is easy to dispose the first rotating member close to the second rotating member in the axial direction to reduce the size of the automatic transmission in the axial direction.
  • a specific gravity of the outer rotating member may be less than a specific gravity of the inner rotating member.
  • inertia of the first rotating member can be easily reduced. Therefore, for example, when the automatic transmission is mounted on a vehicle and is used for changing the gear ratio of the output from an internal combustion engine, the fuel efficiency of the vehicle can be improved.
  • the outer rotating member may be made of an aluminum-based material, and the inner rotating member may be made of a ferrous material.
  • the outer rotating member since the outer rotating member is located radially outward, it is possible to increase torsional resistance, and the torsional resistance can be secured even if the outer rotating member is made of the aluminum-based material which is relatively low in material strength.
  • the inner rotating member since the inner rotating member is located radially inward, it is difficult to increase the torsional resistance, and the torsional resistance is secured by using the ferrous material which is relatively high in material strength. Therefore, it is possible to reduce the inertia while securing the torsional resistance of the first rotating member.
  • the caulking part may be recessed from one of the outer rotating member and the inner rotating member having a higher shearing strength toward the other of the outer rotating member and the inner rotating member having a lower shearing strength.
  • the caulking part is constituted by the one member with the relatively high shearing strength being embedded into the recess formed in the other member.
  • the torsional torque to the first rotating member acts as a force in a shear direction to the embedded part. Therefore, by the part which is embedded in the caulking part being constituted by the one member with the relatively high shearing strength, the strength of the caulking part in the shear direction can be easily improved, and the torsional resistance of the caulking part can be easily increased.
  • the caulking part may be recessed from one of the outer extending part and the inner extending part having a higher coefficient of thermal expansion toward the other of the outer extending part and the inner extending part having a lower coefficient of thermal expansion.
  • the caulking part is constituted by the one member with a relatively high coefficient of thermal expansion being embedded into the recess formed in the other member. Therefore, when the temperature increases, since a thermal expansion allowance of the part embedded into the recess can be increased as compared with a thermal expansion allowance of the recess, it is possible to reduce or prevent rattling or detachment of the caulking part due to the difference in the thermal expansion amount.
  • At least a part of the first extending part other than the caulking part may also overlap with the recess in the axial direction.
  • the automatic transmission can be reduced in size in the axial direction.
  • a power transmission member may be disposed radially inward of the second outer power transmission part, and at least a part of the recess may overlap with the power transmission member in the axial direction.
  • the second rotating member can be disposed close to the power transmission member in the axial direction, while providing the recess in the second extending part. Therefore, the automatic transmission can be further reduced in size in the axial direction.
  • the power transmission member may be a carrier of a planetary gear set.
  • the present disclosure is suitably implementable when the power transmission member is the carrier of the planetary gear set. That is, the second extending part can be disposed close to the planetary gear set in the axial direction.
  • the planetary gear set may have a constituent member made of the same kind of material as the second extending part.
  • the second extending part may be joined to the constituent member by welding.
  • the second extending part and the constituent member of the planetary gear set are made of the same kind of materials, they can be easily joined without using other joining methods, such as spline engagement.
  • the constituent member may be a ring gear.
  • the present disclosure is suitably implementable when the constituent member of the planetary gear set is the ring gear.
  • the first extending part and the second extending part may be located between the planetary gear set and a brake.
  • the brake can be disposed axially close to the planetary gear set. Therefore, the automatic transmission can be further reduced in size in the axial direction.
  • FIG. 1 is a schematic illustration of an automatic transmission according to one embodiment of the present disclosure.
  • FIG. 2 is an engagement table of friction engagement elements of the automatic transmission.
  • FIG. 3 is a cross-sectional view of a third clutch and the periphery thereof.
  • FIG. 4 is a front view of a first rotating member as seen in an A-direction of FIG. 3 .
  • FIG. 5 is a cross-sectional view illustrating a caulking part according to one modification.
  • FIG. 1 is a schematic illustration of an automatic transmission according to one embodiment of the present disclosure.
  • This automatic transmission 1 has, inside a transmission case 2 , an input shaft 3 which is coupled to a drive source and disposed at a drive-source side (left side in this drawing), and an output shaft 4 disposed at an anti-drive-source side (right side in this drawing).
  • the automatic transmission 1 is a longitudinal type for front-engine rear-drive vehicles in which the input shaft 3 and the output shaft 4 are disposed on the same axis O 1 .
  • axial direction Z a direction in which the axis O 1 extends
  • axial direction Z 1 a direction toward the drive-source side in the axial direction Z
  • axial direction Z 2 a direction toward the anti-drive-source side
  • first, second, third, and fourth planetary gear sets (hereinafter, simply referred to as “first, second, third, and fourth gear sets”) PG 1 , PG 2 , PG 3 , and PG 4 are disposed in this order in the axial direction Z 2 side.
  • a first clutch CL 1 , a second clutch CL 2 , and a third clutch CL 3 are disposed in this order in the axial direction Z 1 of the first gear set PG 1 .
  • a first brake BR 1 is disposed on the axial direction Z 1 side of the third clutch CL 3 .
  • a second brake BR 2 is disposed between the third gear set PG 3 and the second gear set PG 2 .
  • Each of the first, second, third, and fourth gear sets PG 1 , PG 2 , PG 3 , and PG 4 is of a single pinion type in which a pinion supported by a carrier directly meshes with a sun gear and a ring gear.
  • the first, second, third, and fourth gear sets PG 1 , PG 2 , PG 3 , and PG 4 have sun gears S 1 , S 2 , S 3 , and S 4 , ring gears R 1 , R 2 , R 3 , and R 4 , and carriers C 1 , C 2 , C 3 , and C 4 , as rotating elements, respectively.
  • the first gear set PG 1 is of a double sun gear type in which the sun gear S 1 is divided into two in the axial direction.
  • the sun gear S 1 has a first sun gear S 1 a disposed at the axial direction Z 1 side, and a second sun gear S 1 b disposed at the axial direction Z 2 side.
  • the first and the second sun gears S 1 a and S 1 b have the same number of teeth, and mesh with the same pinion supported by the carrier C 1 . Therefore, the first and second sun gears Sla and S 1 b carry out the same rotation.
  • the sun gear S 1 of the first gear set PG 1 (in detail, the second sun gear S 1 b ) is coupled to the sun gear S 4 of the fourth gear set PG 4 .
  • the ring gear R 1 of the first gear set PG 1 is coupled to the sun gear S 2 of the second gear set PG 2 .
  • the carrier C 2 of the second gear set PG 2 is coupled to the carrier C 4 of the fourth gear set PG 4 .
  • the carrier C 3 of the third gear set PG 3 is coupled to the ring gear R 4 of the fourth gear set PG 4 .
  • the input shaft 3 is coupled to the carrier C 1 of the first gear set PG 1 through between the first sun gear Sla and the second sun gear S 1 b .
  • the output shaft 4 is coupled to the carrier C 4 of the fourth gear set PG 4 .
  • the first clutch CL 1 is disposed between the input shaft 3 and the carrier C 1 of the first gear set PG 1 , and the sun gear S 3 of the third gear set PG 3 to engage and disengage therebetween.
  • the second clutch CL 2 is disposed between the ring gear R 1 of the first gear set PG 1 and the sun gear S 2 of the second gear set PG 2 , and the sun gear S 3 of the third gear set PG 3 to engage and disengage therebetween.
  • the third clutch CL 3 is disposed between the ring gear R 2 of the second gear set PG 2 and the sun gear S 3 of the third gear set PG 3 to engage and disengage therebetween.
  • the first brake BR 1 is disposed between the transmission case 2 and the sun gear S 1 of the first gear set PG 1 (in detail, the first sun gear Sla) to engage and disengage therebetween.
  • the second brake BR 2 is disposed between the transmission case 2 and the ring gear R 3 of the third gear set PG 3 to engage and disengage therebetween.
  • the automatic transmission 1 engages in one of a first to eighth gear in a D range and a reverse gear in an R range by a combination of engagement states of the first clutch CL 1 , the second clutch CL 2 , the third clutch CL 3 , the first brake BR 1 , and the second brake BR 2 .
  • FIG. 3 is a cross-sectional view illustrating the periphery of the third clutch CL 3 and the second gear set PG 2 , where only one side of the automatic transmission 1 in the radial direction with respect to the input shaft 3 (see FIG. 1 ) is illustrated (upper part in FIG. 1 ).
  • the third clutch CL 3 includes a clutch hub 10 , a clutch drum 20 disposed coaxially at an outer circumferential side of the clutch hub 10 , a plurality of friction plates 6 disposed between the clutch hub 10 and the clutch drum 20 in the radial direction, and a piston part 7 which presses the plurality of friction plates 6 in the axial direction Z 1 so that the plurality of friction plates 6 are brought into contact with each other.
  • the third clutch CL 3 includes a first rotating member 30 which couples the clutch hub 10 to the sun gear S 3 of the third gear set PG 3 (see FIG. 1 ), and a second rotating member 40 which couples the clutch drum 20 to the ring gear R 2 of the second gear set PG 2 .
  • the second rotating member 40 is located radially inward of the first rotating member 30 , and is adjacent to the first rotating member 30 in the axial direction Z at a first extending part 39 and a second extending part 49 which will be described later.
  • the clutch hub 10 has a hub first cylindrical part 11 having a cylindrical shape centering on the axis O 1 , a hub second cylindrical part 13 located coaxially at an outer circumferential side of the hub first cylindrical part 11 , and a hub vertical wall part 15 which radially connects end parts of the hub first cylindrical part 11 and the hub second cylindrical part 13 on the axial direction Z 1 side.
  • a hub first spline part 12 with which some of the plurality of friction plates 6 (friction plates 6 a , hereinafter referred to as “hub-side friction plates”) are engaged so as to be movable in the axial direction Z is formed.
  • a hub second spline part 14 which gives and receives power to and from the first rotating member 30 is formed.
  • the clutch drum 20 has a drum cylindrical part 21 located radially outward of the hub first cylindrical part 11 and radially inward of the hub second cylindrical part 13 .
  • the drum cylindrical part 21 is formed in a cylindrical shape centering on the axis O 1 .
  • a drum spline part 22 with which the remaining friction plates 6 b (hereinafter, referred to as “drum-side friction plates”) of the plurality of friction plates 6 are engaged so as to be movable in the axial direction Z is formed.
  • the friction plates 6 are constructed so that the hub-side friction plates 6 a and the drum-side friction plates 6 b are provided alternately in the axial direction Z.
  • the piston part 7 reciprocates in the axial direction Z by operation hydraulic pressure supplied to a cylinder (not illustrated).
  • a cylinder not illustrated
  • the piston part 7 moves in the axial direction Z 1
  • the plurality of friction plates 6 are pinched between a pressing part 7 a at a tip end of the piston part 7 and the hub vertical wall part 15 so that the third clutch CL 3 becomes in an engaged state.
  • the piston part 7 moves in the axial direction Z 2
  • the plurality of friction plates 6 are released from the engaged state, and therefore, the third clutch CL 3 becomes in a disengaged state.
  • the first rotating member 30 has a first outer rotating member 31 located radially outward, and a first inner rotating member 36 located radially inward of the first outer rotating member 31 , and these members are joined by mechanical clinching (described later).
  • the first outer rotating member 31 and the first inner rotating member 36 are made of different materials.
  • the first outer rotating member 31 is made of a material with a relatively low specific gravity (e.g., an aluminum-based material or a magnesium-based material)
  • the first inner rotating member 36 is made of material with a relatively high specific gravity (e.g., ferrous material).
  • the first outer rotating member 31 has a first outer cylindrical part 32 extending coaxially with the axis O 1 , and a first outer extending part 33 which is bent from an end part of the first outer cylindrical part 32 on the axial direction Z 2 side, and extends radially inward. Moreover, in an inner circumferential part of an end part of the first outer cylindrical part 32 on the axial direction Z 1 side, a first outer spline part 34 which is engaged with the hub second spline part 14 of the clutch hub 10 , and gives and receives power to and from the clutch hub 10 is formed. That is, the first outer cylindrical part 32 constitutes a first outer power transmission part according to the present disclosure.
  • the first inner rotating member 36 has a first inner extending part 37 which extends in the radial direction between the second brake BR 2 and the second gear set PG 2 , and a first inner cylindrical part 38 formed in a cylindrical shape centering on the axis O 1 .
  • the first inner extending part 37 is a plate-like member which is a wrought product of a ferrous material formed in an annular shape.
  • the first inner cylindrical part 38 is formed by forging the ferrous material, and has a flange part 38 a extending radially at an end part on the axial direction Z 1 side.
  • a first inner spline part (not illustrated) which is spline-engaged with an inner circumferential part of the sun gear S 3 of the third gear set PG 3 (see FIG. 1 ), and gives and receives power to and from the sun gear S 3 is formed. That is, the first inner cylindrical part 38 constitutes a first inner power transmission part according to the present disclosure.
  • the first inner rotating member 36 is made by abutting welding the first inner extending part 37 and the flange part 38 a of the first inner cylindrical part 38 in the radial direction.
  • the entire first inner rotating member 36 is made of the ferrous material, but the manufacturing cost like, for example, the case where the entire first inner rotating member 36 is formed by forging, can be reduced.
  • the first inner extending part 37 contacts the first outer extending part 33 from the axial direction Z 2 side at a contact area X 1 .
  • the first outer rotating member 31 and the first inner rotating member 36 are mechanically joined in the axial direction Z at the contact area X 1 with a caulking part 51 via mechanical clinching.
  • the first outer extending part 33 and the first inner extending part 37 are joined to each other to constitute the first extending part 39 .
  • the first extending part 39 is located between the second brake BR 2 and the second gear set PG 2 in the axial direction Z, and extends in the radial direction.
  • the caulking part 51 is recessed from the first inner extending part 37 side to the first outer extending part 33 side (i.e., to the axial direction Z 1 side) to be caulked.
  • the caulking part 51 has a protrusion 51 a which protrudes to the axial direction Z 1 side more than a part of the first outer extending part 33 other than the caulking part 51 .
  • the caulking part 51 is formed by a first inner recess 37 a where the first inner extending part 37 is recessed to the axial direction Z 1 side being embedded into a first outer recess 33 a where the first outer extending part 33 is recessed to the axial direction Z 1 side.
  • FIG. 4 is a front view of the first rotating member 30 as seen in A-direction of FIG. 3 .
  • the contact area X 1 is formed in an annular shape having a width or thickness L 1 in the radial direction around the axis O 1 .
  • Caulking parts 51 are formed at a plurality of locations on a virtual circle C which passes through a substantially middle position of the contact area X 1 in the radial width L 1 , at a substantially equal interval.
  • the number of caulking parts 51 is set in consideration of the joining strength per caulking part 51 against a torsional torque needed between the two rotating elements. Specifically, the number of caulking parts 51 is set in consideration of the strength in a shear direction (rotational direction) of the first inner recess 37 a embedded in the first outer recess 33 a . In this embodiment, since the first inner recess 37 a made of the ferrous material is embedded into the caulking part 51 , it is easier to increase the shearing strength at the embedded part, and it is easier to increase the joining strength of the caulking part 51 as compared with a case where the first outer recess 33 a made of the aluminum-based material is embedded.
  • the second rotating member 40 has a similar structure to the first rotating member 30 , and has a second outer rotating member 41 which is made of an aluminum-based material and a second inner rotating member 46 which is made of a ferrous material and is located radially inward of the second outer rotating member 41 .
  • the second outer rotating member 41 is formed integrally with the clutch drum 20 , and gives and receives power to and from the plurality of drum-side friction plates 6 b through the drum spline part 22 . Therefore, the second outer rotating member 41 constitutes a second outer power transmission part according to the present disclosure.
  • the second outer rotating member 41 has a second outer cylindrical part 42 which continues from the drum cylindrical part 21 and extends to the axial direction Z 2 side, and a second outer extending part 43 which is bent from the end part of the second outer cylindrical part 42 on the axial direction Z 2 side and extends radially inward.
  • the second outer extending part 43 is located on the axial direction Z 1 side of the first extending part 39 and overlaps with the ring gear R 2 of the second gear set PG 2 in the axial direction Z. Moreover, the second outer extending part 43 extends to near the outer diameter part of the ring gear R 2 in the radial direction.
  • the second inner rotating member 46 has a second inner extending part 47 which is made of a drawing material, and a second inner cylindrical part 48 which is made of a forging material, and these are abutted in the radial direction and joined by welding.
  • the second inner extending part 47 extends in the radial direction at the axial direction Z 1 side of the first extending part 39 .
  • the second inner cylindrical part 48 is supported by the flange part 38 a of the first inner cylindrical part 38 in the axial direction Z 1 through a bearing 61 , and is rotatably supported by an inner circumferential part of the first inner cylindrical part 38 through a bearing 62 .
  • a recess 45 is formed in a radially outside part of the second inner extending part 47 , which is recessed to the axial direction Z 1 side in an annular shape centering on the axis O 1 .
  • the recess 45 is located radially outward of the carrier C 2 of the second gear set PG 2 , and at least a part thereof overlaps with the carrier C 2 by a length Y 1 in the axial direction Z.
  • the recess 45 overlaps with at least a part of the protrusion 51 a of the caulking part 51 by a length Y 2 in the axial direction Z.
  • the recess 45 overlaps with at least a part of the first outer extending part 33 other than the caulking part 51 by a length Y 3 in the axial direction Z.
  • the second inner extending part 47 contacts the second outer extending part 43 from the axial direction Z 2 side at a contact area X 2 in a radially outside part of the recess 45 .
  • the second outer rotating member 41 and the second inner rotating member 46 are mechanically joined to each other in the axial direction Z at the contact area X 2 with the caulking part 52 via mechanical clinching.
  • the caulking part 52 is caulked, similarly to the caulking part 51 , by being recessed from the second inner extending part 47 side to the second outer extending part 43 side (i.e., to the axial direction Z 1 side).
  • the caulking part 52 has a protrusion 52 a which protrudes to the axial direction Z 1 side more than a part of the second outer extending part 43 other than the caulking part 52 .
  • the caulking part 52 is formed by a second inner recess 47 a where the second inner extending part 47 is recessed to the axial direction Z 1 side being embedded into a second outer recess 43 a where the second outer extending part 43 is recessed to the axial direction Z 1 side.
  • the second extending part 49 is constituted by joining the second outer extending part 43 and the second inner extending part 47 together.
  • the second extending part 49 overlaps with the ring gear R 2 by a length Y 4 in the axial direction Z.
  • the caulking part 52 is formed at a plurality of locations on a virtual circle which passes through a substantially center position of the radial width in the contact area X 2 at a substantially equal interval.
  • the ring gear R 2 is made of the ferrous material which is the same kind of material as the second inner rotating member 46 .
  • the second inner extending part 47 is joined to the ring gear R 2 from the axial direction Z 2 side by welding at a part of the recess 45 radially inward of the contact area X 2 , and gives and receives power to and from the ring gear R 2 . Therefore, the part of the second inner extending part 47 radially inward of the recess 45 constitutes a second inner power transmission part according to the present disclosure.
  • the automatic transmission 1 according to the embodiment described herein has the following effects:
  • the first rotating member 30 can be constituted by appropriately joining the first outer rotating member 31 and the first inner rotating member 36 , which are made of different materials, at the caulking part 51 .
  • the first rotating member 30 can be set so that each part is made of the suitable material, it is possible to reduce the weight, while securing the strength.
  • the first outer rotating member 31 and the first inner rotating member 36 can be joined, for example, without accompanying the formation of the spline-engagement teeth and without using subsidiary materials, the cost can be reduced. Note that, although the operation and effects described above are similarly demonstrated in the second rotating member 40 , effects of the first rotating member 30 are mainly described in detail below.
  • the protrusion 51 a is formed in the caulking part 51 of the first extending part 39 , which joins the first outer extending part 33 to the first inner extending part 37 , at least a part of the protrusion 51 a is located inside the recess 45 formed in the second extending part 49 .
  • the first extending part 39 can be disposed close to the second extending part 49 , while preventing the protrusion 51 a of the caulking part 51 from interfering with the second extending part 49 . Therefore, it is possible to dispose the first rotating member 30 close to the second rotating member 40 in the axial direction, and it is possible to reduce the size of the automatic transmission 1 in the axial direction Z.
  • the inertia of the first rotating member 30 can be reduced. Therefore, for example, when the automatic transmission 1 is mounted on a vehicle and is used for changing the gear ratio of the output from an internal combustion engine, the fuel efficiency of the vehicle can be improved.
  • the first outer rotating member 31 is made of the aluminum-based material, and the first inner rotating member 36 is made of the ferrous material. Therefore, since the first outer rotating member 31 is located radially outward, it is possible to increase torsional resistance, and the torsional resistance can be secured, even if the first outer rotating member 31 is made of an aluminum-based material which is relatively low in the material strength. On the other hand, since the first inner rotating member 36 is located radially inward, it is difficult to increase torsional resistance, and therefore, the torsional resistance is secured by using the ferrous material which is relatively high in the material strength. Therefore, it is possible to reduce the inertia, while securing the torsional resistance of the first rotating member 30 .
  • the caulking part 51 is formed by being recessed from the first inner rotating member 36 which is made of the ferrous material and is relatively high in the shearing strength toward the first outer rotating member 31 which is made of the aluminum-based material and is relatively low in the shearing strength.
  • the caulking part 51 is constituted by the first inner recess 37 a with the relatively high shearing strength being embedded into the first outer recess 33 a formed in the first outer rotating member 31 .
  • the torsional torque to the first rotating member 30 acts as a force in the shear direction to the embedded part.
  • the part which is embedded in the caulking part 51 being constituted by the first inner rotating member 36 with the relatively high shearing strength, the strength of the caulking part 51 in the shear direction can be easily improved, and the torsional resistance of the caulking part 51 can be easily increased.
  • the first extending part 39 other than the caulking part 51 also overlaps with the recess 45 in the axial direction Z, the first extending part 39 can be disposed closer to the second extending part 49 . Therefore, the automatic transmission 1 can be reduced in size in the axial direction Z.
  • the second gear set PG 2 is disposed radially inward of the second rotating member 40 , and at least the part of the recess 45 overlaps with the carrier C 2 of the second gear set PG 2 in the axial direction Z.
  • the second rotating member 40 can be disposed close to the second planetary gear set PG 2 in the axial direction Z, while providing the recess 45 in the second extending part 49 . Therefore, the automatic transmission 1 can be reduced in size in the axial direction Z.
  • the second gear set PG 2 has the ring gear R 2 made of the ferrous material which is the same kind of material as the second inner rotating member 46 , and the second inner extending part 47 of the second inner rotating members 46 is joined to ring gear R 2 by welding, at the radially inward part of the recess 45 . Since the second inner extending part 47 and the ring gear R 2 are made of the ferrous materials which are the same kind of materials, they can be joined easily without using other joining methods, such as spline engagement.
  • the first extending part 39 and the second extending part 49 are located between the gear set PG 2 and the second brake BR 2 . Since the first extending part 39 and the second extending part 49 are disposed close to the gear set PG 2 in the axial direction Z, it is possible for the second brake BR 2 to also be disposed close to the gear set PG 2 in the axial direction Z. Therefore, the automatic transmission 1 can be reduced in size in the axial direction Z.
  • a caulking part 510 may be caulked from a first outer extending part 330 side made of the aluminum-based material with a relatively low shearing strength to a first inner extending part 370 side made of the ferrous material with a high shearing strength.
  • the caulking part 510 is caulked from the first outer extending part 330 side made of the aluminum-based material with a relatively high coefficient of thermal expansion to the first inner extending part 370 side made of the ferrous material with a relatively low coefficient of thermal expansion.
  • the caulking part 510 is constituted by a first outer recess 331 of the first outer extending part 330 with a relatively high coefficient of thermal expansion being embedded into a first inner recess 371 formed in the first inner extending part 370 with a relatively low coefficient of thermal expansion. Therefore, when the temperature rises, since a thermal expansion allowance of the first outer recess 331 embedded into the first inner recess 371 can be increased as compared with a thermal expansion allowance of the first inner recess 371 , it is possible to reduce or prevent rattling or detachment of the caulking part 510 due to the difference in the thermal expansion amount.
  • the first outer extending part 330 may contact the first inner extending part 370 from the axial direction Z 2 side, a protrusion 511 of the caulking part 510 may protrude to the axial direction Z 1 side, and at least a part of the protrusion 511 may overlap with a recess 450 of a second inner extending part 470 in the axial direction Z.
  • the rotating members which give and receive power between the given rotating element and the third clutch CL 3 are the first rotating member 30 and the second rotating member 40
  • the rotating members are not limited to this configuration.
  • the present disclosure may be suitably implemented when the rotating members included in the first clutch CL 1 , the second clutch CL 2 , the first brake BR 1 , and the second brake BR 2 are each comprised of a radially outside part and a radially inside part which are made of different materials, these parts are joined at the caulking part via mechanical clinching, and the rotating members are adjacent to each other in the axial direction Z.
  • the rotating member which constitutes a part of the clutch or the brake is formed by joining members made of different materials in the axial direction at a caulking part via mechanical clinching to reduce the size of the automatic transmission in the axial direction.
  • the technology described herein may be used suitably in the manufacturing technology field of vehicles in which automatic transmissions are mounted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)
  • General Details Of Gearings (AREA)
US17/033,304 2019-10-18 2020-09-25 Automatic transmission Active US11199246B2 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160160964A1 (en) * 2013-09-09 2016-06-09 Aisin Aw Co., Ltd. Transmission device
US20180306307A1 (en) * 2017-04-20 2018-10-25 Toyota Jidosha Kabushiki Kaisha Transmission
US20190178271A1 (en) 2017-12-08 2019-06-13 Toyota Jidosha Kabushiki Kaisha Joint structure

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003106428A (ja) * 2001-09-28 2003-04-09 Jatco Ltd 自動変速機
JP2015068458A (ja) * 2013-09-30 2015-04-13 アイシン・エィ・ダブリュ株式会社 動力伝達装置
JP6210017B2 (ja) 2014-04-17 2017-10-11 マツダ株式会社 自動変速機
JP6156347B2 (ja) * 2014-12-10 2017-07-05 マツダ株式会社 自動変速機
DE102017130478A1 (de) * 2017-02-24 2018-08-30 Schaeffler Technologies AG & Co. KG Einschubmodul, Hybridmodul, Antriebsstrang für ein Kraftfahrzeug und Verfahren zum Zusammenbauen eines Antriebsstrangs
JP6455542B2 (ja) * 2017-04-20 2019-01-23 マツダ株式会社 自動変速機の摩擦締結装置
JP6648746B2 (ja) * 2017-11-08 2020-02-14 マツダ株式会社 電気抵抗圧入接合構造
JP2019143707A (ja) * 2018-02-20 2019-08-29 マツダ株式会社 自動変速機
JP6958445B2 (ja) * 2018-03-15 2021-11-02 マツダ株式会社 自動変速機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160160964A1 (en) * 2013-09-09 2016-06-09 Aisin Aw Co., Ltd. Transmission device
US20180306307A1 (en) * 2017-04-20 2018-10-25 Toyota Jidosha Kabushiki Kaisha Transmission
US20190178271A1 (en) 2017-12-08 2019-06-13 Toyota Jidosha Kabushiki Kaisha Joint structure
JP2019104018A (ja) 2017-12-08 2019-06-27 トヨタ自動車株式会社 接合構造

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DE102020126983A1 (de) 2021-04-22
DE102020126983B4 (de) 2023-03-16
JP7230773B2 (ja) 2023-03-01
JP2021067288A (ja) 2021-04-30
CN112682482B (zh) 2023-05-23
US20210116004A1 (en) 2021-04-22

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